US7367300B2 - Electric valve drive with a rotating actuator - Google Patents

Electric valve drive with a rotating actuator Download PDF

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Publication number
US7367300B2
US7367300B2 US11/450,325 US45032506A US7367300B2 US 7367300 B2 US7367300 B2 US 7367300B2 US 45032506 A US45032506 A US 45032506A US 7367300 B2 US7367300 B2 US 7367300B2
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US
United States
Prior art keywords
control shaft
pressure element
valve drive
inertia
valve
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US11/450,325
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English (en)
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US20060278190A1 (en
Inventor
Johannes Meyer
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication date
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Assigned to BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT reassignment BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MEYER, JOHANNES
Publication of US20060278190A1 publication Critical patent/US20060278190A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/024—Belt drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
    • F01L2009/2125—Shaft and armature construction
    • F01L2009/2126—Arrangements for amplifying the armature stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/22—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by rotary motors

Definitions

  • the present invention relates to a valve drive of an internal combustion engine that operates according to the “rotating actuator principle.”
  • Such a valve drive is known from German Patent DE 101 40 461 A1.
  • the camshaft is driven mechanically by the crankshaft via a control chain or a control belt.
  • a considerable advantage would be achieved by individually triggering the valves of the individual cylinders or at least the intake valves and outlet valves of the individual cylinders.
  • an electromagnetic valve drive In an electromagnetic valve drive, an “actuator unit” is assigned to each valve and/or each “valve group” of a cylinder. Different basic types of actuator units are currently being researched. In one basic type, an opening magnet and a closing magnet are assigned to one valve or one valve group.
  • valves can be displaced axially, i.e., opened and/or closed, by applying electric current to the magnets.
  • valve drives are difficult to control from the standpoint of control technology.
  • a control shaft with a cam is provided, whereby the control shaft can be pivoted back and forth by an electric motor. This is also referred to as the so-called “rotating actuator principle.”
  • the cam acts on a rocker arm. Then the opening force generated by the cam is applied by the rocker arm to the valve.
  • a lever-like element is also provided in the form of a “hand crank.” Furthermore, a spring clip is also provided, having a protruding spring arm that presses against the lever-like element.
  • the spring arm of the pivoting lever exerts a torque on the control shaft and/or on the cam. The torque depends on the position of the lever-like element, i.e., the pivot position of the control shaft.
  • the control shaft together with the cam in the case of a valve drive like that described in German Patent DE 101 40 461 A1 pivots cyclically back and forth. A reversal of direction of rotation is thus occurring constantly.
  • the electric motor here must accelerate the control shaft and the cam and the lever-like element attached thereto out of the resting state to a relatively high rotational speed.
  • the electric motor is supported by the spring clip in opening the valve, it must work against the force of the locking spring, which requires a relatively high electric power.
  • One essential problem here is that the electric motor “starts” from the resting state each time in acceleration of the control shaft, the cam and the lever-like element of the electric motor connected to the control shaft.
  • the object of the present invention is to create an electric valve drive that operates according to the “rotating actuator principle” which is improved with regard to the electric power consumption.
  • the starting point for the present invention is a valve drive for an internal combustion engine with a valve that is arranged so that it is axially displaceable between an open position and a closed position. Due to a locking spring, the valve is prestressed in the direction of its closed position. Furthermore, a control shaft is provided with a cam which operates the valve. The control shaft is coupled to an electric motor that pivots the control shaft back and forth about a longitudinal axis. Furthermore, a pivotably mounted “pressure element” prestressed by a spring is provided. The pressure element prestressed by the spring exerts a torque on the control shaft. The torque exerted instantaneously on the control shaft depends on the pivot position of the cam. In the back and forth movement of the control shaft, the pressure element is also pivoted back and forth about its pivot axis.
  • the present invention is based on the finding that the power required for operation of the valve and/or the electric power required for valve operation depends to a significant extent on the ratio of the moments of mass inertia of the “pivotable valve drive components.”
  • the acceleration of the control shaft and the cam is supported by the pressure element prestressed by the spring. When the valve is closed, then the spring is maximally stressed.
  • the mass moment of inertia of the pressure element in particular and/or the mass moment of inertia formed by the spring and the pressure element have a decisive effect on the electric power required for operation of the electric motor.
  • a good “electric efficiency” is achieved when the mass moment of inertia of the pressure element in relation to its pivot axis is greater than the mass moment of inertia formed by the control shaft and the cam in relation to the longitudinal axis of the control shaft.
  • the pressure element is designed to be “more solid” than would actually be necessary for transmission of the prestressing force generated by the spring.
  • the maximum rotational speed of the electric motor could be reduced with an increase in the mass moment of inertia of the control shaft and the cam.
  • the dynamics of the valve drive decreases with an increase in the mass moment of inertia of the control shaft and the cam because the mass moment of inertia of the control shaft and the cam must first be accelerated electrically by the electric motor and then must additionally be accelerated mechanically by the springs because the mass moment of inertia of the control shaft and of the cam must also be accelerated even in the “stable end positions,” i.e., from the resting positions of the control shaft. Likewise, this mass moment of inertia must be accelerated electrically in the case of a “mini stroke operation.”
  • an increase in the mass moment of inertia of the pressure element has the advantage that the pressure element need not be accelerated out of the resting position by the electric motor alone when opening the valve but instead is also moved by the spring element.
  • Another advantage achieved with the present invention lies in the fact that the average rotational speed of the electric motor with this invention is shifted into a higher rotational speed range. Therefore, the ohmic losses are reduced, especially in acceleration of the electric motor from low rotational speeds, thus resulting in an improvement in overall electric efficiency. The total power consumption declines and the amount of lost heat to be dissipated is thus also reduced.
  • the spring element is a torsion spring.
  • This may be a torsion spring rod whose first end is fixedly clamped, e.g., being attached to an actuator housing with the pressure element attached to its other end and protruding essentially perpendicularly away from the torsion spring rod.
  • the torsion spring rod may be arranged in parallel with respect to the control cam which is thus a very space-saving arrangement.
  • the “elevated” mass moment of inertia of the pressure element is preferably achieved by a mass concentration at the end distal from the torsion spring. This yields a relatively high mass moment of inertia with a comparatively low total mass of the pressure element.
  • the pressure element may be manufactured from a plate-shaped component, for example, and may have a closed contour with a recess in the central area. The pressure element may be a punched part. The recess may be punched out of the central area in particular.
  • the mass moment of inertia of the pressure element in relation to its pivot axis is greater than the mass moment of inertia formed by the control shaft and the cam and in relation to the longitudinal axis of the control shaft.
  • An especially favorable mass moment of inertia ratio is obtained when the mass moment of inertia of the pressure element in relation to its pivot axis is greater by a factor in the range between 1.7 and 2.3 than the mass moment of inertia formed by the control shaft and the cam and in relation to the longitudinal axis of the control shaft.
  • FIG. 1 shows an electric valve drive with a rotating actuator according to the state of the art as known from DE 101 40 461 A1;
  • FIG. 2 shows a pressure element under prestress by a torsion spring according to an embodiment of the present invention
  • FIG. 3 shows an rpm-angle-of-rotation diagram to illustrate the potential energy savings achieved with the present invention.
  • FIG. 1 shows a rotating actuator such as that known from DE 101 40 461 A1.
  • the content of DE 101 40 461 A1 is herewith fully incorporated into the content of the present patent application. It is herewith pointed out explicitly that all features described in DE 101 40 461 A1 are also the subject matter of the present patent application.
  • FIG. 1 shows an electric valve drive 1 based on the rotating actuator principle.
  • An axially displaceable valve 2 is prestressed by a locking spring 3 into the closed position shown here.
  • a rocker arm 4 is arranged at the shaft end of the valve 2 .
  • a control shaft 5 is provided with a cam 6 acting on the rocker arm 4 .
  • the control shaft 5 with the cam 6 is pivoted back and forth by an electric motor 7 .
  • a lever-like element 8 is provided, an arm 9 of a spring clip 10 pressing against this element.
  • the spring clip 10 thus exerts a torque on the control shaft 5 , this torque being a function of the pivot position of the control shaft 5 .
  • the arm 9 of the spring clip 10 is also moved according to the movement of the lever-like element 8 .
  • the mass moment of inertia of the arm 9 of the spring clip 10 is comparatively low in comparison with the control shaft 5 and the cam 6 .
  • a reduction in the motor power required for valve control i.e., a reduction in electric power required for valve control
  • a reduction in electric power required for valve control can be achieved by using an “arm” and/or a “pressure element” that cooperates with the lever element 8 and has a “higher” mass inertia.
  • the maximum motor rpm and/or idling rpm of the electric motor required for the valve control may be reduced. In other words, this results in an improved overall electric efficiency.
  • FIG. 2 shows an improved arrangement according to the present invention.
  • the arrangement according to FIG. 2 has a torsion rod 11 , one end 12 of which is fixedly clamped, e.g., on an actuator housing (not shown in detail here).
  • a “pressure element 14 ” is attached, pressing against a lever-like element 15 that is fixedly connected to the control shaft 5 and thus is pivoted back and forth together with the control shaft 5 by an electric motor (not shown in FIG. 2 ).
  • the lever-like element 15 is arranged eccentrically with respect to the control shaft 5 .
  • the pressure element 14 has a high mass moment of inertia with respect to its pivot axis, i.e., with respect to the longitudinal axis of the torsion rod 11 , this mass moment of inertia being achieved primarily through a local “mass concentration” in the area of the free end 16 of the pressure element.
  • the mass moment of inertia of the pressure element 14 is larger than the mass moment of inertia formed by the control shaft 5 and the lever-like element 15 and in relation to the longitudinal axis 17 .
  • the pressure element has a comparatively small total mass, which is achieved by means of a recess 18 in the central area of the pressure element 14 .
  • the pressure element 14 is thus formed by a closed contour.
  • FIG. 3 shows a diagram in which the rotational speed of the control shaft is plotted as a function of the angle of rotation of the control shaft.
  • curve 21 corresponds to the conditions in a rotating actuator according to the state of the art as illustrated in FIG. 1 , for example.
  • the shape of curve 22 corresponds qualitatively to a rotating actuator according to the present invention. When the valve is completely closed and the control shaft and the cam are in their resting positions, this corresponds to an angle of rotation of 0. In the range between 0 and ⁇ 1 the control shaft and the cam are accelerated by the electric motor and by the spring, i.e., the pressure element.
  • the pressure element has a comparatively low mass inertia.
  • the control shaft and the cam connected to it must be accelerated to a relatively high rotational speed n 1 .
  • the maximum rotational speed required for valve operation can be reduced to n 2 if the mass moment of inertia of the pressure element is increased in relation to the pivot axis of the pressure element, in particular if it is greater than the mass moment of inertia formed by the control shaft and the cam and in relation to the longitudinal axis of the control shaft.
  • the “actuator motor curve” is much flatter.
  • the “average” operating rotational speed at which the electric motor operates is greater than that in the state of the art when working with a pressure element having a greater mass inertia.
  • the average working rotational speed of a rotating actuator according to the present invention may in fact be smaller.
  • the average operating rotational speed is greater in relation to the maximum motor rotational speed and/or on the idling rotational speed.
  • the ratio between the average operating rotational speed and the maximum motor rotational speed n 1 and/or n 2 is in turn the decisive factor in the “economic viability” of the electric motor.
  • On the whole the overall electric efficiency is better due to an increase in the mass inertia of the pressure element, i.e., with a flatter characteristic line for the rotational speed over the angle of rotation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US11/450,325 2003-12-12 2006-06-12 Electric valve drive with a rotating actuator Expired - Fee Related US7367300B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10358936A DE10358936A1 (de) 2003-12-12 2003-12-12 Elektrischer Ventiltrieb mit Drehaktuator
DE10358936.8 2003-12-12
PCT/EP2004/012432 WO2005061863A1 (de) 2003-12-12 2004-11-03 Elektrischer ventiltrieb mit drehaktuator

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/012432 Continuation WO2005061863A1 (de) 2003-12-12 2004-11-03 Elektrischer ventiltrieb mit drehaktuator

Publications (2)

Publication Number Publication Date
US20060278190A1 US20060278190A1 (en) 2006-12-14
US7367300B2 true US7367300B2 (en) 2008-05-06

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ID=34638715

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/450,325 Expired - Fee Related US7367300B2 (en) 2003-12-12 2006-06-12 Electric valve drive with a rotating actuator

Country Status (6)

Country Link
US (1) US7367300B2 (de)
EP (1) EP1700012B1 (de)
JP (1) JP4538466B2 (de)
CN (1) CN100439664C (de)
DE (2) DE10358936A1 (de)
WO (1) WO2005061863A1 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4049092B2 (ja) * 2003-12-12 2008-02-20 トヨタ自動車株式会社 動弁装置
DE102004054773B4 (de) * 2004-11-12 2006-12-28 Bayerische Motoren Werke Ag Vorrichtung zur Regelung des Hubverlaufes eines Gaswechselventils einer Brennkraftmaschine
DE102006005944A1 (de) * 2006-02-09 2007-08-23 Bayerische Motoren Werke Ag Verbrennungsmotor mit einem elektrischen Ventiltrieb
DE102006023654B3 (de) * 2006-05-18 2007-10-25 Esa Patentverwertungsagentur Sachsen-Anhalt Gmbh Anordnung zur Erzeugung einer nichtlinearen Kraft- bzw. Drehmomentkennlinie
AT508871B1 (de) * 2009-10-09 2012-12-15 Franz Ing Kutschi Variabler ventiltrieb mit verstellbaren nockenwellenantrieb und kipphebeln
GB0920152D0 (en) 2009-11-18 2009-12-30 Camcon Ltd Rotary electromagnetic actuator
CN101886562A (zh) * 2010-06-30 2010-11-17 龚文资 汽车发动机可变配气相位与可变气门升程控制系统
CN102155271A (zh) * 2011-04-01 2011-08-17 王平 无节气门发动机控制装置
WO2020125970A1 (en) * 2018-12-19 2020-06-25 Jaguar Land Rover Limited Engine valve actuation

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2608675A1 (fr) 1986-12-23 1988-06-24 Renault Dispositif de commande d'entrainement en rotation, notamment pour une distribution variable de moteur thermique
EP0347211B1 (de) 1988-06-14 1993-12-08 Honda Giken Kogyo Kabushiki Kaisha Steueranordnung für den Ventilbetrieb einer Brennkraftmaschine
US5327856A (en) * 1992-12-22 1994-07-12 General Motors Corporation Method and apparatus for electrically driving engine valves
US5873335A (en) 1998-01-09 1999-02-23 Siemens Automotive Corporation Engine valve actuation control system
DE19860451A1 (de) 1998-12-28 2000-06-29 Heinz Leiber Antrieb für ein Ventil eines Verbrennungsmotors
EP1136660A1 (de) 2000-03-09 2001-09-26 MAGNETI MARELLI S.p.A. Elektromagnetischer Aktuator mit Spielausgleichseinrichtung für Ventile in einer Brennkraftmaschine
US20020066176A1 (en) 2000-08-01 2002-06-06 Rudolf Paasch Method for the manufacture of an electromagnetic actuator
DE10140461A1 (de) 2001-08-17 2003-02-27 Bayerische Motoren Werke Ag Drehaktor-Vorrichtung zur Hubsteuerung eines Gaswechselventils im Zylinderkopf einer Brennkraftmaschine
WO2003019582A1 (fr) 2001-08-30 2003-03-06 Moving Magnet Technologies (M.M.T.) Actionneur electromagnetique a deux positions stables de fin de course, notamment pour la commande de vannes de conduits d'admission d'air pour moteurs a combustion interne
FR2834118A1 (fr) 2001-08-30 2003-06-27 Moving Magnet Tech Mmt Actionneur electromagnetique a deux positions stables de fin de course, notamment pour la commande de vannes de conduits d'admission d'air pour moteurs a combustion interne

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Publication number Priority date Publication date Assignee Title
US3261338A (en) * 1964-07-13 1966-07-19 Automobile Racing Club Of Okla Valve timing mechanism
DE19825964A1 (de) * 1998-06-10 1999-12-16 Schaeffler Waelzlager Ohg Ventiltrieb einer Brennkraftmaschine
DE19913742A1 (de) * 1999-03-26 2000-09-28 Bayerische Motoren Werke Ag Vorrichtung zur Hubverstellung eines Gaswechselventils im Zylinderkopf einer Brennkraftmaschine
DE19948204A1 (de) * 1999-10-07 2001-04-12 Heinz Leiber Elektromagnetischer Aktuator

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2608675A1 (fr) 1986-12-23 1988-06-24 Renault Dispositif de commande d'entrainement en rotation, notamment pour une distribution variable de moteur thermique
EP0347211B1 (de) 1988-06-14 1993-12-08 Honda Giken Kogyo Kabushiki Kaisha Steueranordnung für den Ventilbetrieb einer Brennkraftmaschine
US5327856A (en) * 1992-12-22 1994-07-12 General Motors Corporation Method and apparatus for electrically driving engine valves
US5494007A (en) 1992-12-22 1996-02-27 General Motors Corporation Method and apparatus for electrically driving engine valves
US5873335A (en) 1998-01-09 1999-02-23 Siemens Automotive Corporation Engine valve actuation control system
DE19860451A1 (de) 1998-12-28 2000-06-29 Heinz Leiber Antrieb für ein Ventil eines Verbrennungsmotors
EP1144813B1 (de) 1998-12-28 2003-04-16 Heinz Leiber Antrieb für ein ventil eines verbrennungsmotors
EP1136660A1 (de) 2000-03-09 2001-09-26 MAGNETI MARELLI S.p.A. Elektromagnetischer Aktuator mit Spielausgleichseinrichtung für Ventile in einer Brennkraftmaschine
US20020066176A1 (en) 2000-08-01 2002-06-06 Rudolf Paasch Method for the manufacture of an electromagnetic actuator
DE10140461A1 (de) 2001-08-17 2003-02-27 Bayerische Motoren Werke Ag Drehaktor-Vorrichtung zur Hubsteuerung eines Gaswechselventils im Zylinderkopf einer Brennkraftmaschine
WO2003019582A1 (fr) 2001-08-30 2003-03-06 Moving Magnet Technologies (M.M.T.) Actionneur electromagnetique a deux positions stables de fin de course, notamment pour la commande de vannes de conduits d'admission d'air pour moteurs a combustion interne
FR2834118A1 (fr) 2001-08-30 2003-06-27 Moving Magnet Tech Mmt Actionneur electromagnetique a deux positions stables de fin de course, notamment pour la commande de vannes de conduits d'admission d'air pour moteurs a combustion interne

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Title
German Search Report dated Dec. 7, 2004 (Four (4) pages).
International Search Report dated Feb. 3, 2005 including English Translation (Fourteen (14) pages).

Also Published As

Publication number Publication date
CN100439664C (zh) 2008-12-03
JP4538466B2 (ja) 2010-09-08
EP1700012A1 (de) 2006-09-13
WO2005061863A1 (de) 2005-07-07
EP1700012B1 (de) 2007-04-11
JP2007514093A (ja) 2007-05-31
DE10358936A1 (de) 2005-07-07
CN1890460A (zh) 2007-01-03
DE502004003508D1 (de) 2007-05-24
US20060278190A1 (en) 2006-12-14

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